KR20010042710A - Turbocharged internal combustion engine - Google Patents
Turbocharged internal combustion engine Download PDFInfo
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- KR20010042710A KR20010042710A KR1020007011430A KR20007011430A KR20010042710A KR 20010042710 A KR20010042710 A KR 20010042710A KR 1020007011430 A KR1020007011430 A KR 1020007011430A KR 20007011430 A KR20007011430 A KR 20007011430A KR 20010042710 A KR20010042710 A KR 20010042710A
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- pressure turbine
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- internal combustion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/24—Control of the pumps by using pumps or turbines with adjustable guide vanes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/004—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust drives arranged in series
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/013—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in series
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/02—EGR systems specially adapted for supercharged engines
- F02M26/08—EGR systems specially adapted for supercharged engines for engines having two or more intake charge compressors or exhaust gas turbines, e.g. a turbocharger combined with an additional compressor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
- F02M26/42—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
- F02B29/04—Cooling of air intake supply
- F02B29/0406—Layout of the intake air cooling or coolant circuit
- F02B29/0412—Multiple heat exchangers arranged in parallel or in series
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
- F02M26/02—EGR systems specially adapted for supercharged engines
- F02M26/09—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine
- F02M26/10—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine having means to increase the pressure difference between the exhaust and intake system, e.g. venturis, variable geometry turbines, check valves using pressure pulsations or throttles in the air intake or exhaust system
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
Abstract
본 발명은 터보과급되는 내연기관(10)에 관한 것으로, 이 내연기관은 적어도 하나의 고압 단계(20)와 상기 고압 단계(20)의 하류 방향으로 배치되는 적어도 하나의 저압 단계(30)와, 파이프 스위치(70,71)를 갖고 엔진(10)의 배기편(12)을 저압 터빈(31)의 입구편에 연결하는 바이패스 파이프(24a,24b)와, 엔진(10)의 작동 변수를 감지하기 위한 센서를 포함하여 구성된다. 상기 고압 터빈(21)은 항상 최저 배기량으로 작동하여 이는 연속적으로 순환하고, 중앙 처리 장치(CPU)가 구비되어 상기 센서의 신호를 받아들이며, 상기 CPU는 파이프 스위치(70,71)가 전체 배기량의 변화 가능한 부분이 고압 터빈(21)과 저압 터빈(31)과 엔진(10)의 새로운 공기편으로 분배되어 흐르도록 작동하게 하여 연료 소모와(또는) 배기량을 최소화할 수 있도록 엔진(10)의 작동 모드를 모두 최적화하도록 한다.The present invention relates to a turbocharged internal combustion engine (10), which comprises at least one high pressure stage (20) and at least one low pressure stage (30) disposed downstream of the high pressure stage (20), Bypass pipes 24a and 24b having pipe switches 70 and 71 connecting the exhaust piece 12 of the engine 10 to the inlet piece of the low pressure turbine 31 and the operating parameters of the engine 10 are sensed. It is configured to include a sensor for. The high pressure turbine 21 always operates at the lowest displacement, which continuously circulates, and is equipped with a central processing unit (CPU) to receive signals from the sensor, and the CPU allows the pipe switches 70 and 71 to change the total displacement. The operating mode of the engine 10 so that the possible parts are distributed and flow into the new air pieces of the high pressure turbine 21 and the low pressure turbine 31 and the engine 10 to minimize fuel consumption and / or displacement. Try to optimize all of them.
Description
두 단계의 과급과정을 가지는 그러한 내연기관은 DE 195 14 572 A1에 개시되어 있는데, 고압의 단계와 저압의 단계가 내연기관의 저속 범위에 있는 터보 과급기(Turbocharger)에 연계 설정된다. 초기의 배기는 고압 터빈으로 그 다음 저압 터빈으로 흐른다. 터보과급된 공기는 먼저 저압 압축기에 의하여 압축된 후 고압압축기에 의하여 압축되고, 열 교환기에서 냉각된 후 내연기관의 새로운 공기 쪽으로 주입된다. 내연기관의 순환 속도가 증가됨에 따라 저압 압축기에서만 압축되는 단일 단계의 압축 과정으로 변환되는데, 따라서, 고압 터빈은 배기편 파이프 스위치에 의하여 완전히 바이패스되고, 고압 압축기는 터보과급하는 공기편 파이프 스위치에 의하여 완전히 바이패스될 수 있다.Such an internal combustion engine having a two-step supercharging process is disclosed in DE 195 14 572 A1, in which the high and low pressure stages are linked to a turbocharger in the low speed range of the internal combustion engine. The initial exhaust flows to the high pressure turbine and then to the low pressure turbine. The turbocharged air is first compressed by a low pressure compressor and then by a high pressure compressor, cooled in a heat exchanger and then injected into the new air of the internal combustion engine. As the circulation speed of the internal combustion engine increases, it is converted into a single stage compression process, which is compressed only in low pressure compressors, so that the high pressure turbine is completely bypassed by the exhaust pipe switch, and the high pressure compressor is connected to the turbocharged air pipe switch. Can be bypassed completely.
그러나 그러한 터보과급하는 과정에서의 변환은 자주 부하를 상승시키고 내연기관의 속도 변화를 발생시키며, 자주 그러한 변화가 터보과급하는 장치 작동의 하나의 단계와 두개의 단계 사이에서 발생되어야 하는 단점이 있었다. 따라서, 승차감의 손실과 연속적이지 못한 가속과 제동 파워 반응이 발생하는 것이다.However, the conversion in such turbocharging process often raises the load and produces a change in the speed of the internal combustion engine, and often such a change has to occur between one and two stages of turbocharging device operation. Thus, a loss of riding comfort and non-continuous acceleration and braking power reactions occur.
청구항 서론에 따른 내연기관은 또한 DE 39 03 563 C1에도 개시되어 있다. 그러나, 상기 특허에서도 터보과급함에 있어서 두 단계에서 한 단계로의 변환이 일어나는데, 이러한 변환은 출구편과 고압 터빈사이에 설치된 파이프 스위치에 의하여 일어나고, 따라서 여기서도 승차감의 손실이 발생한다.An internal combustion engine according to the introduction to the claims is also disclosed in DE 39 03 563 C1. However, in the above patent, the turbocharging takes place from two stages to one stage, which is caused by a pipe switch installed between the outlet piece and the high-pressure turbine, and thus also a loss of ride comfort.
본 발명은 청구항 1의 서론에 기술된 바와 같은 터보 과급(過給)된 내연기관에 관한 것으로, 특히 적어도 하나의 고압과 저압으로의 압력저하 단계를 가지는 터보 과급된 내연기관에 관한 것이다.이때 이 터빈은 싱글 플로(Single Flow),또는 더블 플로(Double Flow)형으로 형성될 수 있고, 또한 고압 터빈의 입구편은 엔진의 배기편에, 그리고 출구편은 저압터빈에 연결될 수 있으며, 입구편의 엔진 배기편을 저압터빈에 연결하는 파이프 스위치에 의하여 잠금가능한 적어도 하나의 바이패스 채널(Bypass Channel)을 포함할 수 있다.The present invention relates to a turbocharged internal combustion engine as described in the introduction of claim 1, and more particularly to a turbocharged internal combustion engine having at least one pressure reduction stage at high and low pressures. The turbine may be formed in a single flow or double flow type, and the inlet side of the high pressure turbine may be connected to the exhaust side of the engine, and the outlet side may be connected to the low pressure turbine. It may include at least one bypass channel (Bypass Channel) lockable by a pipe switch connecting the exhaust piece to the low pressure turbine.
도 1a는 쌍을 이루는 바이패스 흐름을 가지는 두 단계로 터보과급되는 디젤 내연기관의 배기 및 새로운 공기의 플로를 나타낸 순환 다이어그램,1A is a circulation diagram showing the exhaust and fresh air flow of a turbocharged diesel internal combustion engine in two stages with a paired bypass flow;
도 1b는 공통의 바이패스 흐름을 가지는 두 단계로 터보 과급되는 디젤 내연기관의 배기 플로 나타낸 순환 다이어그램,1B is a circulation diagram showing the exhaust flow of a diesel internal combustion engine turbocharged in two stages with a common bypass flow;
도 2는 이중 플로의 저압 터빈을 위한 쌍을 이루는 바이패스 흐름을 가지는 두 단계로 터보과급되는 디젤 내연기관의 배기 플로를 나타낸 순환 다이어그램,2 is a circulation diagram showing the exhaust flow of a turbocharged diesel internal combustion engine in two stages with a paired bypass flow for a dual flow low pressure turbine;
도 3은 저압 바이패스부를 가지는 도 1a에 따른 배기 및 새로운 공기의 플로를 나타낸 순환 다이어그램,3 is a circulation diagram showing the flow of exhaust and fresh air according to FIG. 1A with a low pressure bypass;
도 4는 두 단계로 터보 과급되는 V형 디젤 내연기관의 배기 및 새로운 공기의 플로를 나타낸 순환 다이어그램,4 is a circulation diagram showing the exhaust and fresh air flow of a V-type diesel internal combustion engine turbocharged in two stages;
도 5와 도 6은 고압 터빈으로 다양한 배열의 터빈이 사용되는 다른 순환 다이어그램,5 and 6 are different circulation diagrams in which various arrangements of turbines are used as high pressure turbines,
도 7은 특별한 바이패스 배치을 개시한 순환 다이어그램이다.7 is a circular diagram illustrating a particular bypass arrangement.
〈도면의 주요부분에 대한 부호의 설명〉<Explanation of symbols for main parts of drawing>
10: 디젤 내연기관 11: 새로운 공기편10: diesel internal combustion engine 11: new air
12: 배기편 13a,b: 실린더열12: exhaust piece 13a, b: cylinder row
20: 고압 단계 21: 고압터빈20: high pressure stage 21: high pressure turbine
22: 고압 압축기 23a,b: 플로(flow)22: high pressure compressor 23a, b: flow
24,24a,b: 바이패스 채널 30: 저압 단계24, 24a, b: bypass channel 30: low pressure stage
31: 저압 터빈 32: 저압 압축기31 low pressure turbine 32 low pressure compressor
33a,b: 플로 34: 바이패스부33a, b: flow 34: bypass section
40: 터보과급공기 냉각기 50: 배기 회귀40: turbocharged air cooler 50: exhaust return
60,61,62,62a,b: 파이프 63,63a,b: 마우스 포인트(Mouth Point)60, 61, 62, 62a, b: pipe 63, 63a, b: mouse point
70,71,72: 파이프 스위치 80: 모터 제어기70, 71, 72: pipe switch 80: motor controller
86: 바이패스 라인 87:파이프 스위치86: bypass line 87: pipe switch
본 발명은 이러한 청구항 1항 서론에 따른 내연기관의 문제점을 해결하기 위한 것으로 급속한 부하에 대응하고, 연속적이고 제동 파워 반응을 일으키지 않는 변속을 위한 것이다. 터보과급 압력은 가속 즉, 차량이 가속될 때 지체되지 않고, 엔진 요구량에 무한하고 다양하게 적용될 수 있도록 하는 것이다.The present invention is to solve the problems of the internal combustion engine according to the introduction of claim 1 to respond to rapid load, and for a shift that does not cause a continuous braking power response. Turbocharge pressure is an acceleration, that is, it does not delay when the vehicle is accelerated, so that it can be applied infinitely and variously to the engine demand.
이러한 본 발명의 목적은 독립 청구항의 특징에 의하여 해결될 수 있다.This object of the invention can be solved by the features of the independent claims.
특히, 본 발명의 특징에 따르면 적어도 어떤 범위까지는 고압 터빈을 통한 연속 플로가 있고, 이 플로는 회전하기 때문에 가속할 때 최저의 터보과급 압력이 생기고, 특히 HP 로터의 회전 속도는 가장 바람직한 초기 수준에 있게 된다. 또한, 각각의 배기 플로는 중심 처리부와 파이프 스위치를 구비한 본 발명의 구성에 따라 고압 터빈, 저압 터빈 또는 새로운 공기편에 각 경우에 요구되는 정도로 공급될 수 있고, 따라서 엔진의 작동모드는 최저연료 소비와 최저 배기량을 갖도록 최적화될 수 있다.In particular, according to a feature of the invention there is a continuous flow through the high-pressure turbine at least to some extent, and because the flow rotates, the lowest turbocharge pressure occurs when accelerating, in particular the rotational speed of the HP rotor is at the most desirable initial level. Will be. In addition, each exhaust flow can be supplied to the high pressure turbine, the low pressure turbine or the new air piece to the extent required in each case according to the configuration of the present invention having a central processing unit and a pipe switch, so that the engine operating mode is the lowest fuel. It can be optimized to have a consumption and the lowest displacement.
부하에 적절히 대응하고 엔진의 회전속도를 증가시킬 수 있도록 고압 터빈은 신속하게 반응하는데, 이는 팽창동작이 고압 터빈 방향으로 이동하기 때문이다. 즉, 파이프 스위치에 의하여 바이패스 채널이 거의 클로즈되어 배기 플로의 대부분이 고압 터빈으로 주입되게 되는 것이다. 부하가 약하고 배기량이 적을때 적은 연료 소비와 낮은 부하, 무엇보다도 배기 대응 압력이 이 작동 범위에서 요구된다면, 배기의 팽창동작은 배기 회귀 후의 파이프 스위치를 적절히 위치시키고 바이패스 채널의 오픈으로 엔진의 회전 속도를 독립적으로 하여 저압 터빈에서 대부분 발생하게 할 수 있다.The high pressure turbine reacts quickly so that it can respond appropriately to the load and increase the engine's rotational speed because the expansion operation moves in the direction of the high pressure turbine. That is, the bypass channel is almost closed by the pipe switch so that most of the exhaust flow is injected into the high pressure turbine. If low fuel consumption, low load and, above all, exhaust response pressure are required in this operating range when the load is low and the displacement is small, the expansion operation of the exhaust is performed by properly positioning the pipe switch after exhaust return and by rotating the engine by opening the bypass channel. Independent speeds can cause most of the low pressure turbines.
상기 파이프 스위치는 회전 속도, 배기량, 터보과급 압력, 터보과급 공기 온도등의 엔진의 작동특성을 기록하는 모터 전자 시스템에 연결되어 엔진의 작동 상태에 따라 연료 소비량와 배기량을 최소화하는 작동 모드로 제어될 수 있다. 결과적으로, 최저 연료 소비량과 최저 배기량은 최적 상태를 위하여 조정되는 것이다. 대기 상태에 따라 부하 상태와 회전 속도, 최적화된 배기 플로의 분리는 새로운 공기편, 고압 터빈, 저압 터빈에서 형성되게 된다.The pipe switch is connected to a motor electronic system that records the operating characteristics of the engine, such as rotation speed, displacement, turbocharge pressure, turbocharge air temperature, and can be controlled in an operating mode that minimizes fuel consumption and displacement depending on the engine's operating conditions. have. As a result, the lowest fuel consumption and lowest displacement are adjusted for optimum conditions. Depending on the atmospheric conditions, the separation of load conditions, rotational speeds and optimized exhaust flows will be formed in new air planes, high pressure turbines and low pressure turbines.
배기량의 분배가 가능해짐에 따른 또 다른 잇점은 작동 라인이 고압과 저압 압축기의 작동특성에 따라 운행되어 한편으로는 고압축기 효율이 향상되고, 다른 한편으로는 펌핑이 실질적으로 극단의 상태 이하를 유지하게 된다.Another advantage of enabling the distribution of displacement is that the operating line runs according to the operating characteristics of the high and low pressure compressors, on the one hand, which improves the compressor's efficiency, while on the other hand the pumping remains substantially below extreme. Done.
이미 기술된 본 발명의 제 1의 주요 기술과는 달리 본 발명의 제 2의 주요 기술에 따르면 또한 이하의 효과를 얻을 수 있다.Unlike the first main technique of the present invention already described, according to the second main technique of the present invention, the following effects can also be obtained.
내연기관을 저압터빈의 입구편에 연결시키는 바이패스 채널은 절대적으로 필요한 것은 아니다. 두개의 터빈중 하나 - 바람직하게는 고압터빈 - 는 변화가능한 배열을 가질 수 있으며, 무엇보다도 적당한 베인(vane)을 가지는 분배수단을 구비할 수 있다. 예컨대, 고압터빈에 그러한 분배수단이 구비된다면 비록 전체 플로가 고압터빈을 통하더라도 이러한 플로의 비율은 커지거나 적어지도록 조절될 수 있다.The bypass channel connecting the internal combustion engine to the inlet side of the low pressure turbine is not absolutely necessary. One of the two turbines, preferably the high pressure turbine, can have a variable arrangement and, above all, can be provided with distribution means having suitable vanes. For example, if such a distribution means is provided in the high pressure turbine, even if the entire flow is through the high pressure turbine, the ratio of the flow can be adjusted to be larger or smaller.
또한, 파이프 스위치를 구비한 바이패스 파이프가 제공될 수 있는데, 이를 통하여 고압 터빈은 바이패스 되어질 수 있다. 이때 또한 분배수단은 항상 조금 열려 있어 적어도 최저 배기량이 고압 터빈을 통하여 확실히 흐르고, 따라서 항상 적어도 최저의 터보과급 압력이 존재하며, 특히 HP 로터의 회전 속도는 바람직한 초기 수준에 있게 된다. 파이프 스위치에 의하여 부가적인 제어를 할 수도 있다.In addition, a bypass pipe with a pipe switch can be provided, through which the high pressure turbine can be bypassed. The distribution means are also always slightly open so that at least the minimum displacement flows reliably through the high pressure turbine, so there is always at least the lowest turbocharge pressure, in particular the rotational speed of the HP rotor is at the desired initial level. Additional control may be provided by the pipe switch.
어떻든 상기한 두개의 주요 기술중 하나를 사용함에 있어 잇점은 내연기관의 작동 변수가 매우 민감하게 달라질 수 있는 것이다.In any case, the advantage of using one of the two major technologies described above is that the operating parameters of the internal combustion engine can be very sensitively varied.
이하에서는 본 발명의 바람직한 실시예가 첨부한 도면을 참조하여 보다 상세하게 기술된다.Hereinafter, preferred embodiments of the present invention will be described in more detail with reference to the accompanying drawings.
도 1에 도시된 6-실린더 디젤 내연기관(10)은 터보 과급기에 의하여 두 단계로 터보과급된다. 그러기 위하여 고압단계(20)는 단일의 저압단계(30) 전에 배치된다. 고압 터빈(21)과 저압 터빈(31)에 의하여 구동되는 압축기(22,32)에 의하여 새로운 공기는 압축되고, 두개의 터보과급공기 냉각기(40)에서 냉각되며, 배기 회귀 플로(50)의 배기와 일정 퍼센트(_0)로 혼합되어 엔진(10)의 새로운 공기편(11)에 주입된다. 저압 터빈(32)의 로터 직경은 고압 터빈(21)의 로터 직경 보다 큰데, 저압과 고압 터빈의 사이의 로터 직경비(dL,ND/dL,HD)는 1.2 내지 1.8 정도이다. 고압 터빈(21) 이중 플로의 두개의 플로(23a,b)은 입구편에서 각각 파이프(60,61)에 의하여 엔진의 배기편(12)과 연결된다. 출구편에서는 플로(23a,b)은 출구편 파이프(63,64)를 통하여 차례로 단일 플로의 저압 터빈(31) 입구편에 연결되는 공통 파이프(62)에 연결된다. 두개의 터보과급공기 냉각기 중 하나는 물론 생략될 수 있다.The six-cylinder diesel internal combustion engine 10 shown in FIG. 1 is turbocharged in two stages by a turbocharger. To this end, the high pressure stage 20 is arranged before a single low pressure stage 30. The new air is compressed by the compressors 22 and 32 driven by the high pressure turbine 21 and the low pressure turbine 31, cooled in two turbocharged air coolers 40, and exhausted from the exhaust return flow 50. And a certain percentage (_0) is mixed into the new air piece 11 of the engine (10). The rotor diameter of the low pressure turbine 32 is larger than the rotor diameter of the high pressure turbine 21, and the rotor diameter ratio d L, ND / d L, HD between the low pressure and the high pressure turbine is about 1.2 to 1.8. The two flows 23a and b of the dual flow of the high pressure turbine 21 are connected to the exhaust piece 12 of the engine by pipes 60 and 61 at the inlet side, respectively. At the outlet piece, the flows 23a and b are connected to the common pipe 62 which in turn is connected to the inlet piece of the low pressure turbine 31 of a single flow via the outlet piece pipes 63 and 64. One of the two turbocharged air coolers can of course be omitted.
엔진(10)의 작동 상태에 따른 터보 과급기의 최적 적용 상태에서 바이패스 채널(24a,24b)는 고압 터빈(21)의 각각의 플로(23a,b)에 대하여 대칭적으로 배치된다. 그 각각은 배기 엘보우(elbow)의 분리된 파이프(60,61)로 흐르고, 고압 터빈(20)을 우회하여 단일 플로의 저압 터빈(30)에 단일 공급을 위한 공통 파이프(62)로 흐르게 된다. 각각의 바이패스 채널(24a,b)에는 흐름의 하류 방향으로 배치된 파이프 스위치(70,71)가 제공된다. 이러한 구조는 배기 엘보우 또는 고압 터빈의 하우징에 설치될 수도 있고, 슬라이드, 밸브, 플랩등의 유사한 장치의 형상을 가질 수도 있으며, 단일 또는 공통으로 CPU에 의하여 제어될 수도 있다.In the optimum application state of the turbocharger according to the operating state of the engine 10, the bypass channels 24a, 24b are arranged symmetrically with respect to the respective flows 23a, b of the high pressure turbine 21. Each flows into separate pipes 60, 61 of the exhaust elbow and bypasses the high pressure turbine 20 to a common pipe 62 for a single supply to the low pressure turbine 30 in a single flow. Each bypass channel 24a, b is provided with pipe switches 70,71 arranged in the downstream direction of the flow. Such a structure may be installed in the housing of an exhaust elbow or a high pressure turbine, may have the shape of a similar device such as a slide, a valve, a flap, or the like, or may be controlled by a CPU singly or in common.
또한, 배기 회귀 파이프(50)는 압축기(22)에 대하여 상대적으로 새로운 공기편(11)쪽 뒤로 떨어져서 연결된다. 배기중 회귀된 양은 또한 새로운 공기편의 어떤 다른 지점으로 주입될 수 있다. 한편의 파이프 스위치(70)에 의하여 바이패스 채널(24a)는 클로즈되도록 하고, 다른편은 바이패스 채널(24a)이 오픈되도록 하여 부분적인 흐름이 저압 터빈(30)과 배기 회귀 파이프(50)에 필요한 비율(배기 가스 회기 비율≥0)로 분배할 수 있다. 또한, 작동 특성 변수 a1-n 의 기능을 하는 파이프 스위치(70,71,50)의 제어를 위하여 이 파이프 스위치(70,71,50)는 전자 모터 제어기(80)에 연결되는데, 이 모터 제어기는 작동을 위한 배기량의 최적 분배를 가능하게 한다. 바이패스 비율(24a,b)은 달리 조정이 가능하여 전체 배기량 분배가 좀더 자유로울 수 있다.In addition, the exhaust return pipe 50 is connected to the compressor 22 relative to the new air piece 11 back. The amount returned in the exhaust can also be injected into any other point of the fresh air piece. The pipe switch 70 on the one hand allows the bypass channel 24a to be closed and on the other hand the bypass channel 24a to be opened so that a partial flow is applied to the low pressure turbine 30 and the exhaust return pipe 50. It can distribute in the required ratio (exhaust gas recycle ratio≥0). In addition, the pipe switches 70, 71, 50 are connected to the electronic motor controller 80 for the control of the pipe switches 70, 71, 50 functioning as the operating characteristic variables a1-n. Enables optimal distribution of displacement for operation. The bypass ratios 24a and b can be adjusted differently so that the total displacement distribution can be more free.
도 1b에는 내연기관(10)의 다른 실시예가 도시되어 있다. 이는 도 1a와는 터보 과급기의 형태를 달리하고 있다. 즉, 고압 터빈(21)의 출구편 연결이 두개의 바이패스 채널(24a,b)의 마우스 포인트(63)의 공통 파이프(62) 하류쪽에 제공되는데, 도 1a에서는 상류쪽에 제공되는 것이 다르다.1b shows another embodiment of the internal combustion engine 10. This is different from that of the turbocharger in FIG. 1A. That is, the outlet side connection of the high pressure turbine 21 is provided downstream of the common pipe 62 of the mouse point 63 of the two bypass channels 24a and b, which is different from that provided upstream in FIG.
도 2에는 내연기관(10)의 제 3 실시예가 도시되어 있다. 여기서는 저압 터빈(30)이 이중 플로로 형성되어 있다. 저압 터빈(31)의 두개의 채널(33a,b)은 각각 다른 파이프(62a,62b)로부터 제공되고, 따라서 저압 터빈에는 균일하지 않은 흐름이 제공될 수 있다. 바이패스 채널(24a,b)은 또한 각각 다른 플로(33a,33b)로 나누어 흐르게 되는데, 이는 고압 터빈(21)의 플로(23a,b)가 각각 다른 파이프(62a,62b)로 분리되어 연결되는 것과 같다.2 shows a third embodiment of an internal combustion engine 10. Here, the low pressure turbine 30 is formed in double flow. The two channels 33a, b of the low pressure turbine 31 are provided from different pipes 62a, 62b, respectively, so that the low pressure turbine can be provided with an uneven flow. Bypass channels 24a and b are also flowed separately into different flows 33a and 33b, which flows 23a and b of high-pressure turbine 21 into separate pipes 62a and 62b, respectively. Same as
도 3에 도시된 내연기관은 바이패스부(34)을 가지는 저압 터빈(31)을 구비하고 있는데, 상기 바이패스부는 작동 특성 a1-n으로 기능하는 예비압축의 최적화를 위한 파이프 스위치(72)에 의하여 제어될 수 있다. 이는 특히 예컨대, 공간적인 문제로 고압 압축기(22)와 저압 압축기(32) 사이의 압축기 공기의 냉각이 필요없도록 하기 위한 적용(승용차)에 적당하다. 이를 통하여, 예비압축은 저압 단계(30)에 의하여 엔진(10)의 가늠된 파워의 영역에서 의도하는 범위로 제한될 수 있다.The internal combustion engine shown in FIG. 3 has a low pressure turbine 31 having a bypass portion 34, which bypasses the pipe switch 72 for optimization of precompression functioning with operating characteristics a1-n. Can be controlled. This is particularly suitable for applications (passenger cars), for example, to avoid the need for cooling of the compressor air between the high pressure compressor 22 and the low pressure compressor 32 due to space problems. Through this, the precompression can be limited to the intended range in the region of the estimated power of the engine 10 by the low pressure step 30.
파이프 스위치(72)를 구비한 바이패스 파이프(34)을 통하여 아주 작은 저압(31)을 사용할 수 있다. 이는 엔진의 과운행시 제동 파워를 크게 한다. 따라서 엔진의 가속반응은 이와 함께 향상될 수 있다. 또한, 터보 과급과 배기의 대응압력은 어떤 작동 범위에서는 더 감소될 수 있는데,이는 내연기관의 효율을 더 증가시킬 수 있다.Very low pressure 31 can be used through the bypass pipe 34 with the pipe switch 72. This increases the braking power during overrun of the engine. The acceleration response of the engine can thus be improved with this. In addition, the corresponding pressures of the turbocharge and exhaust can be further reduced in some operating ranges, which can further increase the efficiency of the internal combustion engine.
도 4는 내연기관(10)의 제 5 실시예로서 V8형을 도시한 것이다. 각 실린더열(13a,b)은 다른 고압 단계(20)로 분리된다. 단일 플로의 고압 터빈(21)에는 파이프 스위치(70)를 포함하는 바이패스 채널(24)이 제공된다. 양 고압 터빈(21)의 배기편은 저압 터빈(31)의 입구에 공통으로 연결된다. 여기서 두개의 고압 단계(20)의 바이패스 비율은 달리 세팅할 수 있으므로 전체적인 배기량의 분배도 조절할 수 있다. 기술된 바와 같이 파이프 스위치(70)에 의한 배기 흐름의 분리는 고압 터빈(21)과 저압 터빈(31), 배기 회귀(50)에서 가능하다.4 shows the V8 type as the fifth embodiment of the internal combustion engine 10. Each cylinder row 13a, b is separated into another high pressure stage 20. The single flow high pressure turbine 21 is provided with a bypass channel 24 comprising a pipe switch 70. The exhaust piece of the high pressure turbine 21 is commonly connected to the inlet of the low pressure turbine 31. Here, the bypass ratios of the two high pressure stages 20 can be set differently so that the distribution of the overall displacement can also be adjusted. As described, separation of the exhaust flow by the pipe switch 70 is possible in the high pressure turbine 21, the low pressure turbine 31, and the exhaust return 50.
기본적으로 어떤 터빈이라도 단일 플로, 이중 플로로 또는 다양한 터빈 배열을 갖도록 형성될 수 있고, 특히 적당한 베인을 갖는 분배수단이 구비될 수 있다.Basically any turbine can be formed with a single flow, double flow or with a variety of turbine arrangements, in particular a distribution means having suitable vanes.
도 7에 도시된 다이어그램은 도 3의 다이어그램과 유사하다. 그러나, 이는 고압 압축기를 우회하는 바이패스 라인(86)을 포함하고 있다. 또한, 파이프 스위치(87)도 포함하고 있다. 상기 실시예는 특히 고속에서의 모터 효율과 연료 소모, 배기량에 있어 매우 향상되어 디젤 엔진에 유용한 것으로 판명되었다. 결과를 비교해 볼때 기술적 노력도 상대적으로 적게 소모된다.The diagram shown in FIG. 7 is similar to the diagram of FIG. 3. However, it includes a bypass line 86 that bypasses the high pressure compressor. The pipe switch 87 is also included. This embodiment has proved to be particularly useful for diesel engines, with a significant improvement in motor efficiency, fuel consumption and displacement at high speeds. In comparison, the technical effort is also relatively low.
본 발명의 구성은 디젤 내연기관의 모터 효율을 향상시키고 연료 소모와 배기량을 감소시키는데 유용하다.The configuration of the present invention is useful for improving the motor efficiency and reducing fuel consumption and displacement of a diesel internal combustion engine.
Claims (10)
Applications Claiming Priority (4)
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DE19816778 | 1998-04-16 | ||
DE19837978A DE19837978B4 (en) | 1998-04-16 | 1998-08-21 | Air-flow controller in twin stage turbocharged internal combustion engine |
DE19816778.4 | 1998-08-21 | ||
DE19837978.1 | 1998-08-21 |
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KR20010042710A true KR20010042710A (en) | 2001-05-25 |
KR100815590B1 KR100815590B1 (en) | 2008-03-20 |
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KR1020007011430A KR100815590B1 (en) | 1998-04-16 | 1999-04-09 | Turbocharged internal combustion engine |
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-
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BR9909747A (en) | 2000-12-19 |
DE19837978A1 (en) | 1999-11-04 |
DE19837978B4 (en) | 2006-05-18 |
DE69904928T2 (en) | 2003-10-30 |
DE69904928T3 (en) | 2012-07-12 |
KR100815590B1 (en) | 2008-03-20 |
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